Yarn furnisher for winding machines



Nov. 25, 1969 J. B. LAWSON 3,480,218

YARN FURNISHER FOR WINDING MACHINES 2 Sheets-Sheet 1 Filed Dec. 22. 1966FIG.I

INVENTOR. JOHN B. LAWSON ATTORNEYS Nov. 25, 1969 Q LAWSON 3,480,218

YARN FURNISHER FOR WINDING MACHINES Filed Dec. 22, 1966 2 Sheets-Sheet 2INVENTOR. JOHN B. LAWSON BY W4 ATTORNEYS United States Patent YARNFURNISHER FOR WINDING MACHINES John B. Lawson, Barrington, R.I.,assignor to Robison Rayon Company, Inc., Providence, R.I., a corporationof Rhode Island Filed Dec. 22, 1966, Ser. No. 603,925 Int. Cl. B65h59/06 US. Cl. 242-45 9 Claims ABSTRACT OF THE DISCLOSURE This inventionrelates to apparatus for furnishing yarn to winding machines and thelike, wherein the tension on the yarn is selectively controlled as theyarn is taken up by a yarn package. The invention provides positive yarnfeeding means and a differential control system whereby it is possibleto deliver yarn continuously ti a winder at a pre-selected tension,regardless of tension changes which enter the system from externalsources. Further, the invention provides means whereby a uniform tensionmay be maintained on the yarn throughout the build of the yarn package,or the tension may be programmed to increase or decrease, as desired,while the package builds.

Summary of the invention Yarn packages having yarn wound thereon undercontrolled tension, such as uniform tension throughout, are desired invarious textile uses. As is well known, it is often important to haveuniformly tensioned yarn packages in many weaving and knittingprocesses. Moreover, package dyeing particularly of synthetic yarns, isbest accomplished when the yarn is wound on the package uniformly.

In conventional winding machines operating with constant spindle speeds,the tension on the yarn tends to increase as the yarn package builds,i.e. increases in size. This results in undesirable tension variationsthroughout the yarn package. Various furnishing devices have beenproposed for supplying yarns to winding machines under controlledtensions, but they have proven to be unsatisfactory for a variety ofreasons, such as lack of sensitivity, frequent breakdowns, limitedutility, limited control ranges, lack of accuracy in programming, etc.

A primary object of the present invention is to provide an improved yarnfurnisher, based on a new principle, that will feed yarn continuously toa winding mechanism under selectively and accurately controlled tension.

Another object is to provide a furnisher which may be programmed tomaintain a selected uniform yarn tension throughout the build of thepackage or, if desired, will provide a selected variable tension duringthe package build, such tensions being repeatable for successivepackages wound on the winder.

Another object is to provide a yarn furnisher wherein tension variationsin the yarn as it is withdrawn from its source of supply are, forpractical purposes, nullified so that the tension on the yarn as it isdelivered is a function only of the tension imposed by the device.

Another object is to provide mechanism for furnishing yarn in accuratelymeasured selected lengths under predetermined tension to a winder or thelike.

A further object of this invention is to provide automatic yarnfurnishe-r means for a winding machine which controls the rate at whichthe yarn is positively fed to the winder in response to an integratedsignal combining signals originating from two separate differentialsensing means; one means sensing the build up of the yarn package andthe other means sensing the tension in the yarn as it is delivered fromthe positive yarn feeder to the yarn package on the winder.

3,480,218 Patented Nov. 25, 1969 Description of the drawings Otherobjects and advantages of this invention will be evident from thedescription which follows and from the drawings wherein:

FIGURE 1 is a fragmentary view in perspective of a yarn winding deviceequipped with a preferred yarn furnishing mechanism of this invention;and

FIGURE 2 is an enlarged fragmentary view, partly in section, of thevariable speed drive and differential control system, with the sensingarm and impulse transmission linkages shown schematically.

Detailed description Referring to FIGURE 1, a yarn Y is drawn from acone C or other suitable source of supply and is wrapped about spools 2and 3 which are part of the positive yarn feeder 1. Spool 2 is freelyrotatable and is driven by spool 3 through an elastic belt 4. The axisof spool 2 is set at a divergent angle to that of spool 3 so that theyarn will spiral about the spools, and not become entangled, as thefurnisher operates. Spool 2 is known in the art as a Gaudet roll. Sincethe yarn Y is wound several times about the spool combine 2 and 3, theyarn is positively fed without slippage, and tension variations in theyarn as it comes from the supply C are nullified.

Upon leaving the spools 2 and 3, the yarn travels upwardly through aguide eye 5 at the distal end of a pivotable tension sensing arm 6. Fromguide eye 5, the yarn passes downwardly through the guide eye 11 of areciprocatable traverse arm 12 and thence onto the spindle 13 aboutwhich the yarn package 14 is built. Arm 12 is mounted on the traverseframe T which is swingable about its axis 10. The spindle 13 andtraverse frame T may be the components of any-well known yarn winder,such as a Leesona model No. 50, wherein the spindle is driven at aselected constant speed by the usual winding machine drive shaft (notshown).

As the size of package 14 increases, the traverse frame T graduallyswings outward, about its axis 10, in harmony therewith. Meanwhile, therate at which yarn is taken up by the package 14 gradually increases,due to the increase in the diameter of the package. This inventionutilizes the outward movement of frame T to control continuously thespeed at which yarn Y is delivered by spools 2 and 3 to the winder.

As best shown in FIGURE 2, the proximal end of sensing arm 6 is afiixedto a rock shaft 15 mounted within control housing 7. A spiral spring 16has one end fixed to shaft 15 and its other end secured internally of anaxially turnable annular housing 17. Spring 16 urges shaft 15 in acounterclockwise direction, as viewed in FIGURE 2, to cause arm 6 topivot upward, away from spools 2 and 3. The degree of spring load on arm6 may be varied by turning spring housing '17 relative to rock shaft 15.A spring loaded detent 20 is employed to lock housing 17 againstunintentional angular displacement. Spring housing 17 and detent 20 aredisposed externally of control :housing 7 for ready accessibilitythereto. If desired, housing 17 may be provided with a calibrated scaleto facilitate the setting of spring 16 to impose selected spring loadson sensing arm 6.

It will be seen that yarn Y, as it passes from spool 2 to eye 5 to eye11, is formed into a loop, the size of which is determined by theposition of the upwardly urged arm 6. The yarn passing through loop2-5-11 is tensioned by arm 6, the magnitude of such tension being equalto one-half the torque load imposed by spring 16 on the arm. When thepositive yarn feeding rate of spools 2 and 3 equals the yarn take uprate of package 14, arm 6 imposes a uniform, selected tension on theyarn passing through loop 2-5- 11.

Should any differential occur between the rate at which yarn is fed byspools 2 and 3 and the rate at which yarn is taken up by package 14, thesize of this loop of yarn will change, causing or permitting asimultaneous and proportional change in the position of arm 6. If therate at which yarn is taken up by package 14 should exceed the rate atwhich yarn is delivered positively by spools 2 and 3, the loop of yarn2511 will decrease in size, pulling arm 6 downward. By means ofmechanism to be explained, such downward movement of arm 6 will increasethe positive yarn feeding rate of spools 2 and 3. However, should therate at which yarn is taken up by package 14 fall below the rate atwhich yarn is delivered positively by spools 2 and 3, the loop of yarn2-5-11 will increase in size, permitting arm 6 to move upward under theinfluence of spring 16. This upward movement will cause a decrease inthe positive yarn feeding rate of spools 2 and 3, as will be explained.

Upward movement of arm 6, due to an increase in size of the yarn loop,will reduce the tension exerted by the arm on the yarn Y. Downwardmovement of arm 6, caused by a decrease in the size of the yarn loop,will increase tension on yarn Y.

The positive yarn feeder spool 3 is driven from the winding machinedrive shaft (not shown) through pulley 21, affixed to said shaft, belt22, pulley 23, shaft 24 and a variable speed drive comprising Reevespulleys A and B and elastic belt 32 (FIG. 2). Pulley 23 is afiixed tothe end of the rotatable shaft 24, which is suitably supported Withintubing 26 and control housing 7 by bearings. Within housing 7, Reevespulley A, comprising interengaged pulley halves 27 and 28, is suitablyconnected to shaft 24 for rotation therewith. Pulley half 28 is slidablymounted on shaft 24 so that it may be moved axially toward or away frompulley half 27. A vertical arm 30 pivoted at 31 in housing 37 isequipped with bifurcated rounded ends which straddle shaft 24 and restagainst pulley half 28. When arm is moved in a clockwise direction, asshown in FIGURE 2, it slides pulley half 28 toward pulley half 25,thereby increasing the driving diameter 29 of the pulley A. If arm 30 ismoved counterclockwise, the force of elastic belt 32 will cause pulleyhalf 28 to move to the right, axially along shaft 24, to decrease thedriving diameter 29.

A rotatable shaft 33, mounted within htousing 7 above shaft 24, supportsthe Reeves pulley B, which comprises pulley halves 34 and 35. Thediameter of pulley B is adjustable in similar fashion to that of pulleyA. More particularly, pulley half 34 is slidably mounted on shaft 33,and a vertical arm 36, pivotally attached within housing 7 at 37, hasrounded bifurcated ends 40 which straddle shaft 33 and bear againstpulley half 34. When arm 36 is moved clockwise, as shown in FIGURE 2,pulley half 34 moves toward pulley half 35 to increase the diameter ofpulley B. Conversely, if arm 36 is moved counterclockwise, elastic belt32 will force pulley half 34 away from half 35 to decrease the diameterof the pulley.

Spool 3 is affixed to shaft 33, and thus is driven by shaft 24 throughthe variable speed Reeves drive.

A horizontal link 38, having one end pivotally attached to arm 30 andthe other end pivotally attached to arm 36, coordinates the movement ofthe arms. Clockwise movement of arm 30 moves link 38 to the left of FIG-URE 2, and thereby causes arm 36 to move counterclockwise. Conversely,counterclockwise movement of arm 30 results in clockwise movement of arm36.

Arm 36 is urged in counterclockwise direction, as seen in FIGURE 2, by acompression spring 39 which surrounds a guide rod 100. One end of rod100 is pivotally connected to arm 36 by means of block 51, and its otherend is slidably retained within aperture 52 in the wall of housing 7.Since link 38 connects arm 36 to arm 30, spring 39 serves also to biasarm 30 in a clockwise direction. Thus, in the absence of a counteractingforce, spring 39, acting through arms 30 and 36, will cause pulley A toassume its maximum diameter, and will cause pulley B to assume itsminimum diameter. In such condition, spool 3 will rotate at maximumspeed.

A force to oppose and counteract spring 39 is provided by an airamplifier 41. The latter includes a circular cylinder cap 43 fitted overan aperture 42 in the side of housing 7 and a flexible diaphragm 44clamped between the rim of cap 43 and the rim of aperture 41. Thediaphragm 44, which may be of rubber or other flexible material, isfastened to the bottom of a piston 45 by a threaded plug 46. The spacebetween the piston and the cylinder cap 43 provides a hermeticallysealed pressure chamber 48.

Piston 45 has an axial bore 49, which is enlarged and threaded at itsrearward end to receive plug 46. The forward end of bore 49 receives apiston rod 53 which, in turn, is pivotally connected to arm 30 by meansof block 54. Piston 45 is provided at its forward end with an orifice55, which communicates with piston bore 49 via passage in the piston.Bore 49, in turn, communicates with chamber 48 via axial bore 47 in plug46.

Compressed air from a suitable source (not shown) is introduced intochamber 48 via pipe 57 and orifice 58 in cap 43. From chamber 48,compressed air passes to orifice via plug bore 47, piston bore 49 andpiston passage 50. For purposes to be explained, the diameter of orifice58 is smaller than that of orifice 55.

Orifice 55 may be closed or opened by a valve 60 pivotally attached at61 to piston rod 53. Valve 60 is biased clockwise, as seen in FIGURE 2,about its pivot 61, by a compression spring 62 seated in an aperture 63in piston 45. In the absence of a counteracting force, spring 62 pivotsvalve 60 to close orifice 55 to preclude the escape of compressed airtherefrom.

When orifice 55 is closed, air pressure builds up behind piston 45causing it to move to the right of FIG- URE 2. Movement of piston 45 tothe right does not occur until the air pressure in chamber 48 overcomesthe force of spring 39, which acts on piston 45 through arm 36, link 38,arm 30 and rod 53. Since piston rod 53 moves with the piston, it pivotsarm 30 in a counterclockwise direction, permitting the diameter ofpulley A to be reduced. Because of link 38, this movement of arm 30causes clockwise movement of arms 36 to close pulley B and increase itsdiameter. The aforementioned change in diameter size of pulleys A and Bcauses a reduction in the speed of rotation of spool 3.

When valve 60 is moved about its pivot 61 away from orifice 55, thelatter will be opened. If opened sufiiciently, the volume of compressedair escaping from orifice 55 will exceed that entering through orifice58, since the latter is of smaller diameter, and the pressure behind thepiston will drop. When the force exerted by the compressed air on thepiston is reduced below the force exerted by spring 39, the spring actsto urge piston 45 to the left of FIGURE 2. Because spring 39 also movesarms 30 and 36 to the left, the diameter of pulley A will increase andthat of pulley B will decrease, thereby increasing the rotational speedof spool 3.

Accordingly, air amplifier 41, under the control of valve 60, and actingin opposition to the force of spring 39, regulates arms 30 and 36 toadjust the size of Reeves pulleys A and B. The latter, in turn, governthe yarn feeding speed of spool 3. When spool 3 is rotating at thedesired yarn feeding rate, free of external yarn tension influences, thesystem will be in equilibrium. In such condition, valve 60 will openorifice 55 sufficiently to maintain the force exerted by the compressedair on piston 45 equal to the force exerted by spring 39 on the piston.At this time the amount of compressed air escaping from orifice 55 willbe in balance with the amount passing through orifice 58 into chamber48.

Between its maximum speed position, to the far left in FIGURE 2, and itsminimum speed position, to the far right in FIGURE 2 (when valve 60 isclosed), piston 45 will have an infinite number of equilibriumpositions. For each such equilibrium position there is a correspondingspeed of rotation of spool 3, and hence a corresponding yarn feedingrate. As will be explained more fully hereinafter, the equilibriumposition of piston 45 is adjustable automatically to maintain the yarndelivery rate of spools 2 and 3 in pre-selected relationship to the yarntake-up rate of yarn package 14.

Since valve 60 is mounted on piston rod 53, it moves as the pistonmoves. A horizontal flexible link 65 is connected to the upper end ofvalve 60 and, as more fully explained hereinafter, limits the extent ofmovement of the upper end of valve 60 when piston 45 is moved to theright, following closure of orifice 5 5-. As the piston 45 and valve 60move to the right. Link 65 eventually is rendered taut. As a result,while piston 45 continues its movement, link 65 causes valve 60 to pivotcounterclockwise, thereby opening orifice 55 and permitting compressedair to escape therefrom, causing the air pressure behind piston 45 todrop. When orifice 55 is opened sufiiciently to equalize the forceexerted by the compressed air on the piston with the opposing forceexerted thereon by spring 39, a new equilibrium position is reached bythe piston, and it comes to rest.

If link 65 should be moved to the left, as seen in FIG- URE 2, valve 60will be opened beyond its equilibrium position, thereby increasing theescape of compressed air from orifice 55. As a result, the force exertedby the compressed air on piston 45 is reduced, thereby permitting spring39 to move the piston to the left in FIGURE 2. Such movement of piston45 will continue until link 65 becomes slack, whereupon spring 63-causes valve 60 to pivot clockwise to close orifice 55 sufliciently toestablish a new equilibrium position. When this occurs, the piston againcomes to rest.

Thus, link 65 controls valve 60, and thereby determines the equilibriumposition of piston 45, and hence the yarn delivery speed of spool 3.

Horizontal flexible link 65 connects the upper end of valve 60 to avertical link 66 which serves as a differential control means. Link 65may be in the form of a finely fashioned chain, or may comprise a cordof nylon or similar material. Differential control link 66 is pivotallyattached at its lower end to a cam controlled link 68 supported withinhousing 7 by a horizontal pivot 69. The upper end of differential link66 is formed with a rightangled extension 70 slidably engaged within aforked member 71 fastened to rock shaft 15. When the system is inequilibrium, arm 6, acting through shaft 15, fork 71 and differentiallink 66, tensions flexible link 65 sufficiently to urge valve 60counterclockwise, about pivot 61, against spring 62. In such condition,flexible link 65 is tensioned sufliciently to open orifice 55 to theextent necessary to maintain the force exerted by the compressed air onthe piston equal to the force exerted thereon by spring 39.

Movement of arm 6 in a downward direction, caused by the take-up speedof package 14 exceeding the delivery speed of spools 2 and 3, movesdifferential link 66 counterclockwise about its pivot 67. This motionpulls flexible link 65 to the left, as seen in FIGURE 2, pivoting valve60 counterclockwise to open further orifice 55. When the force of theair pressure behind piston 45 becomes less than the force of spring 39,the piston moves to the left, as previously described. Accordingly, thediameter of pulley A is increased and that of pulley B is decreased,causing the rotational speed of shaft 33 and spool 3 to increase, untilthe yarn delivery speed again equals the yarn take-up speed of package14.

As the piston 45 moves to the left, the tension exerted on flexible link65 by differential link 66 is relaxed, permitting spring 62 to biasvalve 60 in a clockwise direction, toward orifice 55. Piston 45continues to move to the left until valve 60 closes orifice 55sufliciently to permit the air pressure behind the piston to build upuntil the force exerted thereby again equals the counteracting forceexerted by spring 39. After piston 45 has moved far enough to permitarms 30 and 36 to make, through the Reeves differential drive, thedesired speed correction, spring 62 restores valve 60 to its equilibriumposition. The piston now comes to rest, and remains in its new positionuntil the next correction.

If arm '6 should move up, caused by the delivery speed of the spools 2and 3 exceeding the take-up speed of package 14, differential link 66will pivot clockwise, about its pivot 67, permitting flexible link 65 torelax. As a result, spring 62 urges valve 60 clockwise, about its pivot61, to close orifice 55. When the force of the air pressure behindpiston 45 exceeds the force of spring 39, the piston moves to the right,as seen in FIGURE 2. This movement reduces the diameter of pulley A andenlarges the diameter of pulley B, thereby reducing the speed of shaft33 and spool 3, until the yarn delivery rate again equals the yarntake-up means.

As piston 45 moves to the right, flexible link 65 will be tensioned,causing valve '60 to begin to pivot counterclockwise to open orifice 55,permitting compressed air to escape again therefrom. Piston 45 continuesto move to the right until valve 60 opens orifice sufliciently to permitthe force of the air pressure behind the piston to be reduced until itis equal to the force exerted by spring 39. At this point, the pistonagain comes to rest, having moved far enough to permit arms 30 and 36 tomake the necessary adjustment of the Reeves differential drive toprovide the desired speed correction.

Thus, arm 6 senses any disparity between the positive yarn feeding rateof the spools 2 and 3 and the yarn takeup rate of the package 14, andtransmits this difference via impulse transmission means comprising rockshaft 15 and fork 71 to differential link 66. The latter transmits theimpulse to valve 60, permitting piston 45 to adjust the Reevesdifferential drive to correct the yarn delivery speed of roll 3. Whenthe disparity between the yarn take-up speed and the yarn delivery speedis eliminated, arm 6 stops its movement. Like piston 45, it remains inits new position until the next speed correction is required.

If external influences which tend to vary the tension on yarn Y enterthe system, the positive yarn feeding spools 2 and 3 will respond,either increasing or decreasing the yarn feeding rate. As a result, arm6 will move to restore the balance between the yarn feeding rate of thespools and the yarn take-up rate of package 14. For example, if yarntension is increased for any reason, thereby slowing down spools 2 and3, arm 6 will be pulled down to speed up spools 2 and 3 to restore thespeed balance. Should external influences cause a reduction of tensionon the yarn, permitting spools 2 and 3 to speed up, arm

6 will rise to slow down the speed of the spools and restore the speedbalance.

The movement of winding frame T in a clockwise direction about its axis10, in response to the build up of the yarn package 14, is utilized tocontrol the speed of the delivery spool 3. There is connected to theframe T a rigid link 74 to which an upstanding link 75 is attached. Link75 is connected to one end of a pivotally mounted horizontal link76(FIG. 1), the opposite end of which is connected to upstanding link 77.The latter is in two sections, which are connected by a turnbuckle 78.At its upper end, link 77 is connected to a lever 81 afiixed to a rockshaft 82 supported within housing 7. Also affixed to rock shaft 82 (FIG.2), for angular movement therewith, is a cam 83 having a curved cam slot84. A pin 85, which acts as a cam follower, is mounted on the lower endof link 68 and engages within cam slot 84.

As the traverse frame T and its link 74 move in a clockwise direction,during the buildup of package 14, link 75 is raised, causing link 77 todescend. The descent of link 77 causes link 81, shaft 82 and cam 83 topivot counterclockwise, thus moving link 68 clockwise about its pivot69. This motion of link 68 causes differential link 66 to pivotclockwise about fork 71, thereby pulling flexible link 65 to the left toopen valve 60. As a result, the air pressure behind piston 45 is reducedand spring 39 causes the piston to move to the left of FIGURE 2. Throughthe motions already explained, this movement of piston 45 increases thediameter of pulley A and decreases the diameter of pulley B, whereby thedelivery speed of spool 3 is increased.

Cam slot 84 is shaped so that, as yarn package 1 4 builds, the impulsetransmission means comprising links 74, 75, 76, 77, lever 81, rock shaft82, cam 83, pin 85 and link 68 actuates differential link 66 to producethe desired change in the speed of rotation of spool 3. Thus, cam 83 isdesigned so that each increment of movement of frame T produces aselected and corresponding increment of change in the speed of spool 3.The design of cam slot 84 may be such as to maintain the yarn deliveryspeed of rolls 2 and 3 equal to the yarn take-up speed of package 14, inwhich event a uniform tension will be maintained on the yarn beingwound. In such case, as frame T moves outward, cam 83 will cause theproper adjustments to be made to the Reeves differential drive, throughdifferential link 66, flexible link 65, air amplifier 41 and arms 30 and36, to increase the speed of spool 3 to the extent required.

However, if it is desired to reduce the tension on the yarn slightly, asit is wound, cam slot 84 is designed to overcorrect the speed of spool3. In such event, as frame T moves outward, cam 83 actuates the speedcontrol system to increase the speed of spool 3 to an extent sufficientto overfeed the yarn. When this occurs, arm 6 rises to reduce thetension on the yarn. As arm 6 rises, it actuates the speed controlsystem to decrease the speed of spool 3 to eliminate the disparitybetween the yarn delivery rate and the yarn take-up rate caused by cam83. When the two rates are again equal, the upward movement of arm 6ceases. Thus, arm 6, as it rises to its new position, eliminates theovercorrection caused by cam 83, restores the yarn delivery and take-upspeed balance and reduces tension on the yarn. In the course of windinga complete package 14, under gradually reducing yarn tension, arm 6gradually rises, through an angle of about 45, from start to finish.

It will be seen that arm 6 has three functions: (1) to apply apre-selected uniform or pre-selected variable tension on the yarn, (2)to nullify the effect of tension variations which enter the yarn feedingsystem from external sources and (3) where a pre-selected variabletension is programmed to control speed overcorrections orundercorrections arising from the movement of frame T, so that the yarnfeeding speed is maintained equal to the yarn take-up speed of package14. In practice, because slight tension variations tend to arisecontinuously, from a variety of causes, arm 6 is constantly oscillatingor vibrating as it carries out its functions. Where uniform tension isto be maintained on the yarn as the package builds, the arm will vibratein a more or less fixed position. Because the arm 6 is constantlyvibrating, it is constructed of light, but rigid, material.

The length of link 77 can be adjusted by turnbuckle 78. In this manner,the angular position of arm 6, when valve 60 is in equilibrium position,may be adjusted as desired. Thus, the length of link 77 can be changedso that arm 6 will activate valve 60 at different angular positions withrespect to the positions of the traverse frame T.

In addition, the connection of link 75 to link 74 can be moved closer orfurther from the axis 10 of the traverse frame T. In this manner, theamount of speed change imparted to spool 3 can be adjusted to equal thechange of take-up speed of the package 14 or to provide speed changeswhich are either greater or less than the requirement of the package 14.If, for example, link 75 is positioned further away from axis 10 of thetraverse frame, the speed of spool 3 will be overcorrected as thepackage builds, and arm 6 will rise to correct for the over-feed. As thearm 6 rises, the force exerted by spring 16 on the arm will decrease,thus reducing the tension on the yarn Y. In this manner also, a reducingtension may be programmed.

It will be noted that arm 6 has an upward extension 88 (FIG. 2) disposedbetween the electrical contacts of an insulated clip 99. If the armrises too high, as would occur if the yarn should break or run out, orif it drops too low, as might happen if the yarn fouls on spool 3,extension 88 will strike a contact and stop the winder. The clip 99 isconnected to a stop motion system (not shown) for stopping the winder ina manner familiar in the art.

Means 89 are provided for measuring the amount of yarn wound on apackage, and is connected by cable 90 to the stop motion system to stopa wind after a selected amount of yarn has been wound. Spool 3 has afixed circumference, and it is thus possible to measure the yarndelivered per revolution of the spool. Counter 89 is mounted on thehousing 7, and is connected to spool 3, to measure the revolutionsthereof, through reduction gearing 91, 92, 93, 94 and 95. The counter 89may be of a pre-set type, of well-known construction, capable of closingan electric contact after a selected count has been obtained. With sucha counter, connected to the stop motion system of the winder, it ispossible to regulate and select the amount of yarn to be wound on agiven package, and to have the wind stop when the selected amount isreached.

Thus, this invention makes possible, for the first time, the provisionof a yarn package wound with a pre-selected length of yarn,automatically and accurately, under a pre-selected, programmed tension,all of which is repeatable for successive packages wound on the machine.

It is to be clearly understood that the terms and expressions usedherein are employed as terms of description, and not of limitation, andthat there is no intention in using such terms and expressions toexclude any equivalents of the apparatus or method described. It is alsoto be clearly understood that what is specifically shown and describedherein represents a preferred embodiment only of the invention, and thatvarious changes and equivalents may be resorted to without departingfrom the principles of the invention or the scope of the claims hereof.Accordingly, it is intended to claim the present invention broadly, aswell as specifically, as indicated in the appended claims.

What is claimed is:

1. A furnisher for feeding a strand of material to the wind package of awinding machine, comprising:

(a) ahousing,

(b) a first shaft rotatably supported by said housing,

(c) an adjustable diameter pulley and a strand feeding spool mountedupon said first shaft for rotation therewith,

(d) a second shaft rotatably supported by said housing,

(e) an adjustable diameter pulley mounted upon said second shaft,

(f) drive means for rotating said second shaft at a speed fixed inrelation to the axial speed of said wind package,

(g) an elastic belt trained about said adjustable diameter pulleyswhereby rotation of said second shaft is transmitted to rotate saidfirst shaft and said strand feeding spool,

(h) hydraulic piston means operable to move and thereby to change thediameter of at least one of said pulleys so as to change the ratio ofthe peripherial speeds of said first and second shafts, and thus theratio between the rotational speed of said spool and the axial speed ofsaid wind package,

(i) control means for said hydraulic piston including a valve operableto adjust the hydraulic pressure 9 upon said piston to govern themovement of said piston, and

(j) a first and a second sensing means for operating said valve, saidfirst means comprising a movable arm supported by said housing forforming said strand into a loop between said spool and said windingpackage and means connecting said arm to said valve so that a change insize of said loop causes movement of said valve; said second sensingmeans comprising means movable in response to a change in diameter ofsaid wind package and connected to said valve so that said change indiameter moves said valve.

2. A yarn furnisher for a winding machine including:

(a) a yarn feeder for delivering y-arn to a winder;

(b) tension sensing means engaging said yarn as it passes from the yarnfeeder to the yarn package being formed on said winder for producing asignal output in response to the tension in said yarn;

(c) a variable speed drive, drivingly connected to said yarn feeder;

(d) a second sensing means engaging said yarn package for producing asignal output in response to the build up of yarn thereon;

(e) impulse transmission means connected to said variable speed drivefor regulating said drive in response input signals; and

(f) means connecting said tension sensing means and said second sensingmeans to each other and to said impulse transmission means forconverting the output signals from said tension sensing means and saidsecond sensing means into a single input signal to said impulsetransmission means.

3. The invention of claim 2 wherein said impulse tranmission meanscomprises an air amplifier.

4. The invention of any one of claims 2 and 3, wherein means areconnected to said yarn feeder for measuring the length of yarndelivered.

5. The invention of any one of claims 2 and 3 wherein said tensionsensing means comprises an arm contacting said yarn and forming saidyarn into a loop as it passes from the feeder to the yarn package andspring means biasing said arm to apply a predetermined tension to saidyarn.

6. The invention of any one of claims 2 and 3 wherein said means forconverting said output signals comprises a first lever pivotallyconnected at one end and having a free end thereof positioned to engagesaid second sensing means and pivot in response to the output signaltherefrom, and a second lever pivotally connected at one end end to thefree end of said first lever and having its other end positioned toengage said tension sensing means and pivot in response to the outputsignal therefrom, and input means connected to said second lever andsaid impulse transmission means movable to a plurality of positions inresponse to movement of said second lever for producing an input signalto said impulse transmission means.

'7. The invention of claim 3 wherein said air amplifier comprisescontinuously pressurize piston and cylinder means including a pistonhaving passage means therethnough communicating with said continuouslypressurized cylinder and terminating in valve means, said valve meansbeing operatively connected to said means for converting said outputsignals to receive said input signal, said piston being operativelyconnected to said variable speed drive.

8. The invention of claim 6 wherein said input means comprises aflexible link connected at one end to said second lever, and linkagemeans connecting the other end of said flexible link to said impulsetransmission means.

9. The invention of claim 7 wherein said means for converting the outputsignals from said tension sensing means and said second sensing meansinto a single input signal to said impulse transmission means comprisesa first lever pivotally connected at one end and having a free endthereof positioned to engage said second sensing means and pivot inresponse to output signal therefrom, and a second lever pivotallyconnected at one end to the free end of said first lever and having itsother end positioned to engage said tension sensing means and pivot inresponse to the output signal therefrom, and input means comprising aflexible link connected at one end to said second lever, and a leverpivotally mounted to said piston having one end forming a flapper forsaid valve means and the other end connected to said flexible link, saidinput means being movable to a plurality of positions in response tomovement of said second lever for producing an input signal to saidimpulse transmiss1on means.

References Cited UNITED STATES PATENTS 2,401,676 6/1946 Weber 242-45 X2,466,109 4/1949 Jencks 24218 2,915,254 12/1959 Weber et a1. 242452,938,365 5/1960 Lassiter 242--45 X 3,047,247 7/1962 Kotte 242453,371,879 3/1968 Hill 24245 NATHAN L. MINTZ, Primary Examiner

